Gas turbine and operating method thereof

ABSTRACT

Provided is a gas turbine capable of achieving high-speed startup of the gas turbine through quick operation control of an ACC system during startup of the gas turbine, improving the cooling efficiency of turbine stationary components, and quickly carrying out an operation required for cat back prevention during shutdown of the gas turbine. Included are a pressurizing device ( 40 ) connected to a branching channel ( 42 ) branching from the discharge side of a compressor ( 11 ) and capable of carrying out an operation for introducing and pressurizing air independently from the compressor ( 11 ); a temperature-control-medium supply channel ( 43 ) that guides compressed air pressurized at the pressuring device ( 40 ) to a turbine-cooling-medium channel ( 50 ) provided in stationary components of a turbine ( 13 ); and a temperature-control-medium return channel ( 44 ) that guides the compressed air that has passed through the turbine-cooling-medium channel ( 50 ) to the discharge side of the compressor ( 11 ) such that the flows are combined, and the pressurizing device ( 40 ) is operated at startup of the gas turbine and in preparation immediately before startup to carry out temperature-raising and cooling by letting the compressed air flow in the turbine-cooling-medium channel ( 50 ). The pressurizing device ( 40 ) is operated during shutdown of the gas turbine to exhaust the high-temperature gas remaining in the turbine ( 13 ).

TECHNICAL FIELD

The present invention relates to a gas turbine and an operation methodthereof and, more specifically, relates to an active clearance control(ACC) system at startup of the gas turbine and to cat-back preventionwhile the gas turbine is shut down.

BACKGROUND ART

A typical gas turbine is constituted of a compressor, a combustor, and aturbine, and air taken in from an air intake port is compressed by thecompressor into high-temperature, high-pressure compressed air. Thecompressed air is supplied to the combustor, and, in the combustor,high-temperature, high-pressure combustion gas is generated by supplyingfuel to the compressed air and combusting it. Since the combustion gasdrives the turbine connected to the compressor, for example, power canbe generated at the generator driven by the gas turbine by connectingthe generator to the output shaft of the gas turbine.

With such a gas turbine, an active clearance control (hereinafterreferred to as ACC) system carries out control to minimize the tipclearance, which fluctuates in response to the effect of temperature andcentrifugal force, which vary in accordance with the operating state,preventing interference between rotary parts and stationary parts andachieving high efficiency in operation.

In general, in a gas turbine in which tip clearance is not controlled,tip clearance is minimized at a startup position, not at a positionduring rated operation. Thus, with the ACC system, an operating statewith minimum tip clearance is set during rated operation by warming upstationary components that affect the tip clearance in a step beforestarting up the gas turbine. In other words, as illustrated in FIGS. 12Ato 12D, the ACC system is a technique for minimizing clearance duringrated operation to ensure the operating efficiency by increasing theclearance in advance by warming up the turbine stationary parts beforestarting up the gas turbine and adjusting the temperature of the turbinestationary parts during rated operation.

The operation of a gas turbine with the above-described ACC system canbe broadly classified into the following five states.

(1) Immediately Before Startup

To apply the ACC system, the stationary components of the turbine statorblades are warmed up by letting a temperature-control medium (heatingmedium) flow therethrough, thus increasing the expansion to increase theclearance between stationary parts, such as a blade ring, and rotorblades, which are rotary parts.

(2) During Startup (while Increasing Load)

In the same manner as immediately before startup, the stationarycomponents continue to be warmed up so that the clearance does notdisappear during startup (so that the stationary parts and the rotaryparts do not contact each other).

(3) During Rated Operation

The clearance between the stationary parts and the rotary parts isminimized by changing the conditions (temperature etc.,) of thetemperature-control medium (heating medium) flowing through thestationary components.

(4) During Shut-Down (while Lowering Load)

In the same manner as immediately before startup, the stationarycomponents continue to be warmed up so that the clearance does notdisappear during shutdown (so that the stationary parts and the rotaryparts do not contact each other).

(5) During Shut-Down

High-temperature gas remaining inside the gas turbine is exhaustedoutside the gas turbine to prevent cat back. Furthermore, thedistribution of gas remaining inside the gas turbine is eliminated byletting the temperature-control medium (heating medium) flow through thestationary components to prevent cat back.

In the above-described ACC system, the clearance control method for thegas turbine is classified into the following three methods.

(1) Control Method Based on Changing the Conditions of the CoolingMedium Flowing Inside the Turbine Blades

This is a control method in which the temperature of the cooling mediumflowing inside the turbine is changed by changing the cooling method forthe cooling medium etc. (for example, changing from no cooling to aircooling or steam cooling), thereby adjusting the clearance by changingthe amount of expansion of the turbine blades themselves, which requiresa mechanism for changing the cooling method for the cooling medium.

(2) Control Method Based on Adjusting the Temperature of StationaryComponents by Steam or Air

This is a method for controlling the clearance by letting steam etc.generated at an exhaust gas boiler flow through the stationarycomponents after adjusting it with valves, etc.; in general, when air isused, the cycle efficiency decreases because the air is discarded to thegas path side without collecting it.

Furthermore, when steam is used, the startup time is long becauseoperation in a simple cycle cannot be achieved, and boiler warm-up isrequired. Moreover, when steam is used, additional equipment isrequired, such as an auxiliary boiler for startup and steam piping fromthe exhaust gas boiler.

(3) Control Method Based on Moving Blades or Casing with a MechanicalMechanism

This is a control method for adjusting the clearance by providing amechanical mechanism, such as an actuator, and moving the blades andcasing.

As related art of the above-described ACC system, compressed air isextracted and, after passing through a flow regulating valve, cools asegmented ring of the stationary components (for example, refer to PTL1).

Furthermore, part of the steam used in the steam turbine is taken outand returned to the steam turbine system after adjustment by a valve andcooling the segmented ring (for example, refer to PTL 2).

In this way, the cat back problem has been noted when the gas turbine isstopped by the ACC system. Cat back is a phenomenon in which, while thegas turbine is stopped, the gas turbine warps due to a temperaturedifference. That is, since temperature layers are formed inside the gasturbine even after it has stopped because the inside of the gas turbinereaches a high temperature during operation, a temperature difference isgenerated between the upper part of the gas turbine (high temperature)and the lower part of the gas turbine (low temperature). As a result,the entire gas turbine warps in a stooping manner due to a difference inthe amount of expansion generated between the upper part and lower partof the gas turbine.

As related art to prevent such cat back, a nozzle is provided on theupper part of a cylinder casing, and cooling air flows toward the upperpart of the wall surfaces in the cylinder to decreases the upper andlower temperature difference (for example, refer to PTL 3).

Furthermore, there is one in which openings are formed in the cylinderlower part and the cylinder upper part to circulate air in the cylinderusing a pump (for example, refer to PTL 4).

CITATION LIST Patent Literature

-   {PTL 1} Japanese Unexamined Patent Application, Publication No.    HEI-6-317184-   {PTL 2} Japanese Unexamined Patent Application, Publication No.    2001-248406-   {PTL 3} Japanese Unexamined Patent Application, Publication No.    2005-171455-   {PTL 4} Japanese Unexamined Patent Application, Publication No.    2002-371806

SUMMARY OF INVENTION Technical Problem

However, with the above-described gas turbine, from the viewpoint ofimproving the operation efficiency of equipment etc., there is a demandfor an increase in the startup speed of the gas turbine. Therefore, alsowith the ACC system during startup of the gas turbine, there is a desirefor achieving an increase in the startup speed of the gas turbine byquickly warming up stationary components to a desired temperature and toexpand them, thus increasing the clearance between stationary parts androtary parts to an optimal value. In such a case, it is desirable thatthe addition of additional equipment can be minimized.

Furthermore, with the above-described gas turbine, there is a demand forimproving the cooling efficiency of the stationary components of theturbine during rated operation. In such a case, it is desirable that theaddition of additional equipment be minimized.

Moreover, for example, a gas turbine that drives a generator is operatedin DSS (daily start-and-stop) mode in order to cope with the powerdemand fluctuation during day time and night time. That is, in such DSSmode, since operation and shutdown of the gas turbine are frequentlycarried out, there is a desire for quickly completing the operationrequired for cat back prevention. Furthermore, for a gas turbineoperated in DSS mode, it is also desirable that the time required forstartup be short. Moreover, it is also desirable to minimize additionalequipment required for cat back prevention.

The present invention has been conceived in light of the above-describedcircumstances, and an object thereof is to provide a gas turbine and astartup operating method thereof in which quick operation control of theACC system is carried out during startup of the gas turbine, and anincrease in the startup speed of the gas turbine is achieved.

Another object of the present invention is to provide a gas turbine andrated-operation operating method thereof that achieve improved coolingefficiency of the stationary components of the turbine in the ACC systemduring rated operation of the gas turbine.

Another object of the present invention is to provide a gas turbine andshutdown operating method thereof that are capable of quickly carryingout the operation required for cat back prevention during shutdown ofthe gas turbine.

Solution to Problem

To solve the above-described problems, the present invention employs thefollowing solutions.

A gas turbine according to a first aspect of the present invention is agas turbine that supplies combustion gas generated by supplying fuel toa combustor where the fuel is combusted with compressed air compressedat a compressor to a turbine to acquire rotational power, the gasturbine including pressurizing means connected to a branching channelbranching from a discharge-side channel of the compressor and capable ofcarrying out an operation for introducing and pressurizing a heatingmedium independently from the compressor; a heating-medium supplychannel that guides pressurized heating medium pressurized at thepressuring means to a turbine-cooling-medium channel provided in astationary component of the turbine; and a heating-medium return channelthat guides the pressurized heating medium that has passed through theturbine-cooling-medium channel to the discharge-side channel such thatthe flows are combined, wherein the pressurizing means is operated atstartup of the gas turbine and in preparation immediately before startupto raise the temperature by letting the pressurized heating medium flowin the turbine-cooling-medium channel.

Such a gas turbine apparatus includes pressurizing means connected to abranching channel branching from a discharge-side channel of thecompressor and capable of carrying out an operation for introducing andpressurizing a heating medium independently from the compressor; aheating-medium supply channel that guides pressurized heating mediumpressurized at the pressuring means to a turbine-cooling-medium channelprovided in a stationary component of the turbine; and a heating-mediumreturn channel that guides the pressurized heating medium that haspassed through the turbine-cooling-medium channel to the discharge-sidechannel such that the flows are combined, wherein the pressurizing meansis operated at startup of the gas turbine and in preparation immediatelybefore startup to raise the temperature by letting the pressurizedheating medium flow in the turbine-cooling-medium channel; therefore,the pressurized heating medium having a raised temperature by beingpressurized at the pressurizing means heats and warms up the stationarycomponents of the turbine while passing through theturbine-cooling-medium channel. At this time, since the pressurizingmeans can be operated independently from the gas turbine main body,rapid clearance control is possible in preparation immediately beforestartup of the gas turbine.

In the above-described aspect, it is desirable that a bypass channelthat branches from a midpoint in the heating-medium supply channel andis connected to the discharge-side channel, and including channelopening/closing means, be further included; in this way, part of thepressurized heating medium having a raised temperature is re-pressurizedand re-heated by letting part of the pressurized heating mediumpressurized at the pressurizing means to raise the temperature thereofflow through the bypass channel by opening the channel opening/closingmeans. Therefore, the temperature of the pressurized heating medium,after pressurization, passing through the turbine-cooling-medium channelis increased even more.

In the above-described aspect, it is desirable that heating means thatcarries out heat exchange with the heating medium or the pressurizedheating medium to raise the temperature be provided in the branchingchannel or the heating-medium supply channel; in this way, thetemperature of the pressurized heating medium can be increased even moreby heating the pressurized heating medium passing through theturbine-cooling-medium channel.

In the above-described aspect, it is desirable to provide aheating-medium branching supply channel that branches from theheating-medium supply channel and that is connected to acompressor-cooling-medium channel in the compressor and a heating-mediumbranching return channel that guides the pressurized heating medium,which has passed through the compressor-cooling-medium channel, to thedischarge-side channel such that the flows are combined; in this way,since, in addition to the temperature of the stationary components ofthe gas turbine, the temperature of the compressor side can also beraised, clearance control of the turbine and the compressor becomespossible.

In the above-described aspect, it is desirable that selective-switchingmeans for the heating medium be provided on an intake side of thepressurizing means; in this way, pressure and temperature can be raisedby introducing a high-temperature heating medium from outside the gasturbine, when necessary.

In the above-described aspect, it is desirable that the pressurizedheating medium pressurized at the pressurizing means be guided to thedischarge-side channel such that the flows are combined after beingconnected in series or parallel with the turbine-cooling-medium channelfor carrying out cooling in the combustor; in this way, in addition toclearance control of the gas turbine, cooling of the combustor can becarried out.

A startup operating method for a gas turbine according to a secondaspect of the present invention is a startup operating method of a gasturbine that supplies combustion gas generated by supplying fuel to acombustor where the fuel is combusted with compressed air compressed ata compressor to a turbine to acquire rotational power, the method, whichis carried out at startup of the gas turbine and in preparationimmediately before startup, including a step in which pressurizingmeans, which is connected to a branching channel branching from adischarge-side channel of the compressor and capable of operatingindependently from the compressor, introduces and pressurizes a heatingmedium; a step in which pressurized heating medium pressurized at thepressurizing means is supplied to a turbine-cooling-medium channelprovided in a stationary component of the turbine to raise thetemperature of the stationary component with the pressurized heatingmedium passing through the turbine-cooling-medium channel; and a step inwhich the pressurized heating medium is guided from theturbine-cooling-medium channel to the discharge-side channel such thatthe flows are combined.

Such an operating method for startup of a gas turbine, which is carriedout at startup of the gas turbine and in preparation immediately beforestartup, includes a step in which pressurizing means, which is connectedto a branching channel branching from a discharge-side channel of thecompressor and capable of operating independently from the compressor,introduces and pressurizes a heating medium; a step in which pressurizedheating medium pressurized at the pressurizing means is supplied to aturbine-cooling-medium channel provided in a stationary component of theturbine to raise the temperature of the stationary component with thepressurized heating medium passing through the turbine-cooling-mediumchannel; and a step in which the pressurized heating medium is guidedfrom the turbine-cooling-medium channel to the discharge-side channelsuch that the flows are combined; therefore, the pressurized heatingmedium pressurized by the pressurizing means to raise the temperaturecan heat and warm up the stationary components while passing through theturbine-cooling-medium channel. At this time, since the pressurizingmeans can be operated independently from the gas turbine main body,clearance control can be quickly carried out in preparation immediatelybefore startup of the gas turbine.

A gas turbine according to a third aspect of the present invention is agas turbine that supplies combustion gas generated by supplying fuel toa combustor where the fuel is combusted with compressed air compressedat a compressor to a turbine to acquire rotational power, the gasturbine including pressurizing means connected to a branching channelbranching from a discharge-side channel of the compressor and capable ofcarrying out an operation for introducing and pressurizing atemperature-control medium independently from the compressor; atemperature-control-medium supply channel that guides pressurizedtemperature-control medium pressurized at the pressuring means to aturbine-cooling-medium channel provided in a stationary component of theturbine; and a temperature-control medium return channel that guides thepressurized temperature-control medium that has passed through theturbine-cooling-medium channel to the discharge-side channel such thatthe flows are combined, wherein the pressurizing means is operatedduring rated operation of the gas turbine to carry out cooling byletting the pressurized temperature-control medium flow in theturbine-cooling-medium channel.

Such a gas turbine includes pressurizing means connected to a branchingchannel branching from a discharge-side channel of the compressor andcapable of carrying out an operation for introducing and pressurizing atemperature-control medium independently from the compressor; atemperature-control-medium supply channel that guides pressurizedtemperature-control medium pressurized at the pressuring means to aturbine-cooling-medium channel provided in a stationary component of theturbine; and a temperature-control medium return channel that guides thepressurized temperature-control medium that has passed through theturbine-cooling-medium channel to the discharge-side channel such thatthe flows are combined, wherein the pressurizing means is operatedduring rated operation of the gas turbine to carry out cooling byletting the pressurized temperature-control medium flow in theturbine-cooling-medium channel; therefore, efficient cooling can becarried out due to the temperature difference between the stationarycomponent of the turbine and the pressurized cooling medium.

In the above-described aspect, it is desirable that the pressurizedtemperature-control medium pressurized at the pressurizing means beguided to the discharge-side channel such that the flows are combinedafter being connected in series or parallel with theturbine-cooling-medium channel for carrying out cooling in thecombustor; in this way, in addition to clearance control of the gasturbine, cooling of the combustor can be carried out.

In the above-described aspect, it is desirable that temperaturecontrolling means that allows temperature control of the pressurizedtemperature-control medium be further included; in this way, therelative temperature difference can be increased even more to improvethe cooling efficiency even more.

In such a case, it is desirable that the temperature controlling meansbe a coolant supply channel that adds a coolant to thetemperature-control-medium supply channel; in this way, the temperatureof the pressurized temperature-control medium pressurized by thepressurizing means to raise the temperature can be lowered by adding acoolant. In this case, the coolant may be liquid or gas.

Furthermore, it is desirable that the temperature controlling means be aheat exchanger that is provided in the branching channel or thetemperature-control-medium supply channel and lowers the temperature ofthe temperature-control medium or the pressurized temperature-controlmedium; in this way, the temperature of the temperature-control mediumbefore pressurization by the pressurizing means or the temperature ofthe pressurized temperature-control medium after pressurization can belowered by the heat exchanger.

In such a case, it is desirable to provide a heating-medium branchingsupply channel that branches from the heating-medium supply channel andthat is connected to a compressor-cooling-medium channel in thecompressor and a heating-medium branching return channel that guides thepressurized heating medium, which has passed through thecompressor-cooling-medium channel, to the discharge-side channel suchthat the flows are combined; in this way, since, in addition to thetemperature of the stationary components of the gas turbine, thetemperature of the compressor side can also be raised, clearance controlof the turbine and the compressor becomes possible.

A rated-operation operating method for a gas turbine according to afourth aspect of the present invention is a rated operation method for agas turbine that supplies combustion gas generated by supplying fuel toa combustor where the fuel is combusted with compressed air compressedat a compressor to a turbine to acquire rotational power, the method,which is carried out during rated operation of the gas turbine,including a step in which pressurizing means, which is connected to abranching channel branching from a discharge-side channel of thecompressor and capable of operating independently from the compressor,introduces and pressurizes a temperature-control medium; a step in whichpressurized temperature-control medium pressurized at the pressurizingmeans is supplied to a turbine-cooling-medium channel provided in astationary component of the turbine and cools the stationary componentwith the pressurized temperature-control medium passing through theturbine-cooling-medium channel; and a step in which the pressurizedtemperature-control medium is guided from the turbine-cooling-mediumchannel to the discharge-side channel such that the flows are combined.

Such a rated-operation operating method for a gas turbine, the method,which is carried out during rated operation of the gas turbine, includesa step in which pressurizing means, which is connected to a branchingchannel branching from a discharge-side channel of the compressor andcapable of operating independently from the compressor, introduces andpressurizes a temperature-control medium; a step in which pressurizedtemperature-control medium pressurized at the pressurizing means issupplied to a turbine-cooling-medium channel provided in a stationarycomponent of the turbine and cools the stationary component with thepressurized temperature-control medium passing through theturbine-cooling-medium channel; and a step in which the pressurizedtemperature-control medium is guided from the turbine-cooling-mediumchannel to the discharge-side channel such that the flows are combined;therefore, efficient cooling can be carried out by the temperaturedifference between the stationary component of the turbine and thepressurized temperature-control medium.

A gas turbine according to a fifth aspect of the present invention is agas turbine that supplies combustion gas generated by supplying fuel toa combustor where the fuel is combusted with compressed air compressedat a compressor to a turbine to acquire rotational power, the gasturbine including pressurizing means connected to a branching channelbranching from a discharge-side channel of the compressor and capable ofcarrying out an operation for introducing and pressurizing atemperature-control medium independently from the compressor; atemperature-control-medium supply channel that guides pressurizedtemperature-control medium pressurized at the pressuring means to aturbine-cooling-medium channel provided in a stationary component of theturbine; and a temperature-control-medium return channel that guides thepressurized temperature-control medium that has passed through theturbine-cooling-medium channel to the discharge-side channel such thatthe flows are combined, wherein a ventilation cooling system in whichthe pressurizing means is operated at shutdown of the gas turbine toexhaust high-temperature gas remaining in the turbine is provided.

Such a gas turbine includes pressurizing means connected to a branchingchannel branching from a discharge-side channel of the compressor andcapable of carrying out an operation for introducing and pressurizing atemperature-control medium independently from the compressor; atemperature-control-medium supply channel that guides pressurizedtemperature-control medium pressurized at the pressuring means to aturbine-cooling-medium channel provided in a stationary component of theturbine; and a temperature-control-medium return channel that guides thepressurized temperature-control medium that has passed through theturbine-cooling-medium channel to the discharge-side channel such thatthe flows are combined, wherein a ventilation cooling system in whichthe pressurizing means is operated at shutdown of the gas turbine toexhaust high-temperature gas remaining in the turbine is provided;therefore, during shutdown of the gas turbine, the high-temperature gasremaining in the turbine is forcefully discharged to the atmosphere toquickly carry out ventilation cooling.

In the above-described aspect, it is desirable that the ventilationcooling system include an exhaust channel branching from thetemperature-control-medium supply channel and having channelopening/closing means and channel opening/closing means provided in thetemperature-control-medium supply channel, downstream of the branchingpoint of the exhaust channel.

Furthermore, in the present invention described above, it is desirablethat the ventilation cooling system include an exhaust channel branchingfrom the branching channel and having channel opening/closing means.

A gas turbine according to a sixth aspect of the present invention is agas turbine that supplies combustion gas generated by supplying fuel toa combustor where the fuel is combusted with compressed air compressedat a compressor to a turbine to acquire rotational power, the gasturbine including pressurizing means connected to a branching channelbranching from a discharge-side channel of the compressor and capable ofcarrying out an operation for introducing and pressurizing atemperature-control medium independently from the compressor; atemperature-control-medium supply channel that guides pressurizedtemperature-control medium pressurized at the pressuring means to aturbine-cooling-medium channel provided in a stationary component of theturbine; and a temperature-control-medium return channel that guide thepressurized temperature-control medium that has passed through theturbine-cooling-medium channel to the discharge-side channel such thatthe flows are combined, wherein the pressurizing means is operated atshutdown of the gas turbine to let the pressurized temperature-controlmedium flow in the turbine-cooling-medium channel.

Such a gas turbine includes pressurizing means connected to a branchingchannel branching from a discharge-side channel of the compressor andcapable of carrying out an operation for introducing and pressurizing atemperature-control medium independently from the compressor; atemperature-control-medium supply channel that guides pressurizedtemperature-control medium pressurized at the pressuring means to aturbine-cooling-medium channel provided in a stationary component of theturbine; and a temperature-control-medium return channel that guide thepressurized temperature-control medium that has passed through theturbine-cooling-medium channel to the discharge-side channel such thatthe flows are combined, wherein the pressurizing means is operated atshutdown of the gas turbine to let the pressurized temperature-controlmedium flow in the turbine-cooling-medium channel; therefore, duringshutdown of the gas turbine, the pressurized temperature-control mediumflows through the turbine-cooling-medium channel in a circulatingmanner, and the temperature distribution of the inside of the gasturbine can be made substantially uniform.

A shutdown operating method for a gas turbine according to a seventhaspect of the present invention is a shutdown operating method for a gasturbine that supplies combustion gas generated by supplying fuel to acombustor where the fuel is combusted with compressed air compressed ata compressor to a turbine to acquire rotational power, the method, whichis carried out at shutdown of the gas turbine, including a step in whichpressurizing means connected to a branching channel branching from adischarge-side channel of the compressor and capable of carrying out anoperation for introducing and pressurizing a temperature-control mediumindependently from the compressor; a step in which pressurizedtemperature-control medium pressurized at the pressurizing means returnsto the discharge-side channel via a temperature-control-medium supplychannel, a turbine-cooling-medium channel, and atemperature-control-medium return channel; and a step in whichexhausting to the atmosphere is carried out from the discharge-sidechannel through the combustor and the turbine.

Such an operating method for shutdown of a gas turbine includes a stepin which pressurizing means connected to a branching channel branchingfrom a discharge-side channel of the compressor and capable of carryingout an operation for introducing and pressurizing a temperature-controlmedium independently from the compressor; a step in which pressurizedtemperature-control medium pressurized at the pressurizing means returnsto the discharge-side channel via a temperature-control-medium supplychannel, a turbine-cooling-medium channel, and atemperature-control-medium return channel; and a step in whichexhausting to the atmosphere is carried out from the discharge-sidechannel through the combustor and the turbine; therefore, duringshutdown of the gas turbine, the high-temperature gas remaining in theturbine is forcefully discharged to the atmosphere to quickly carry outventilation cooling.

An operating method for shutdown of a gas turbine according to an eighthaspect of the present invention is a shutdown operating method for a gasturbine that supplies combustion gas generated by supplying fuel to acombustor where the fuel is combusted with compressed air compressed ata compressor to a turbine to acquire rotational power, the method, whichis carried out at shutdown of the gas turbine, including a step in whichpressurizing means connected to a branching channel branching from adischarge-side channel of the compressor and capable of carrying out anoperation for introducing and pressurizing a temperature-control mediumindependently from the compressor; a step in which pressurizedtemperature-control medium pressurized at the pressurizing means returnsto the discharge-side channel via a temperature-control-medium supplychannel, a turbine-cooling-medium channel, and atemperature-control-medium return channel; and a step in which intake iscarried out from the discharge-side channel through the branchingchannel to the pressurizing means.

Such an operating method for shutdown of a gas turbine includes a stepin which pressurizing means connected to a branching channel branchingfrom a discharge-side channel of the compressor and capable of carryingout an operation for introducing and pressurizing a temperature-controlmedium independently from the compressor; a step in which pressurizedtemperature-control medium pressurized at the pressurizing means returnsto the discharge-side channel via a temperature-control-medium supplychannel, a turbine-cooling-medium channel, and atemperature-control-medium return channel; and a step in which intake iscarried out from the discharge-side channel through the branchingchannel to the pressurizing means; therefore, during shutdown of the gasturbine, the pressurized temperature-control medium flows through theturbine-cooling-medium channel in a circulating manner, and thetemperature distribution of the inside of the gas turbine can be madesubstantially uniform.

An operating method for shutdown of a gas turbine according to a ninthaspect of the present invention is a shutdown operating method for a gasturbine that supplies combustion gas generated by supplying fuel to acombustor where the fuel is combusted with compressed air compressed ata compressor to a turbine to acquire rotational power, wherein, atshutdown of the gas turbine, the shutdown operating method according toClaim 19 is selected when the shutdown period of the gas turbine islong, whereas the shutdown operating method according to Claim 20 isselected when the shutdown period of the gas turbine is short.

With such a shutdown operating method for a gas turbine, at shutdown ofthe gas turbine, the shutdown operating method for a gas turbineaccording to Claim 19 is selected when the shutdown period of the gasturbine is long, whereas the shutdown operating method for a gas turbineaccording to Claim 20 is selected when the shutdown period of the gasturbine is short; therefore, by selecting the operating method forshutdown of a gas turbine according to Claim 20 when the shutdown periodof the gas turbine is short, for example, as in a DSS mode, the insideof the turbine can be maintained substantially evenly at a relativelyhigh temperature, and the warm-up operation time during startup can beshortened.

Advantageous Effects of Invention

According to the present invention described above, quick operationcontrol of the ACC system is carried out at startup of the gas turbineand in preparation immediately before startup, and the startup speed ofthe gas turbine can be increased. In other words, at startup of the gasturbine and in preparation immediately before startup, since ACC controlfor expanding the stationary components by quickly warming them up to adesired temperature and increasing the clearance between the stationaryparts and the rotary parts to an optimal value is possible, startupspeed of the gas turbine can be increased by decreasing the timerequired for startup preparation of the gas turbine, and the equipmentoperating efficiency of the gas turbine is improved.

In this case, the effective use of the pressuring means and so on bysharing them as pressurizing means for boost-up used for closed coolingrealizes high-speed startup of the gas turbine by performing ACC controlwith minimum additional equipment, i.e., without adding new equipment.

According to the present invention, in the ACC system operated duringrated operation of the gas turbine, the cooling efficiency of coolingthe turbine stationary components with a pressurized temperature-controlmedium is improved; therefore, the amount of pressurizedtemperature-control medium used is minimized, and ACC control formaintaining the clearance between the stationary parts and the rotaryparts to a minimum value can be reliably carried out.

In this case, the effective use of the pressuring means and so on bysharing them as pressurizing means for boost-up used for closed coolingenables continuous stable rated operation of the gas turbine byperforming ACC control with minimum additional equipment, i.e., withoutadding new equipment.

According to the present invention, at shutdown of the gas turbine, anoperation required for cat back prevention can be reliably and quicklycarried out by discharging the high-temperature gas in the turbine tothe atmosphere or by maintaining the temperature distribution in theturbine in a substantially uniform state.

In particular, by maintaining the temperature distribution in theturbine in a substantially uniform state by letting a pressurizedtemperature-control medium flow through the turbine-cooling-mediumchannel in a circulating manner, the operation required for cat backprevention can be completed quickly, and the warm-up operation period atstartup can be shortened, even when operation and shutdown of the gasturbine are carried out frequently, such as in a DSS mode.

Furthermore, with regard to additional equipment required for cat backprevention, the effective use of the pressuring means and so on bysharing them as pressurizing means for boost-up used for closed coolingenables stable operation shutdown of the gas turbine by performing ACCcontrol enabling cat back prevention, with minimum additional equipment,i.e., without adding new equipment.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a schematic diagram illustrating a gas turbine according to afirst embodiment of the present invention and a tenth embodiment of thepresent invention.

FIG. 2 is a schematic configuration diagram illustrating a configurationexample of a gas turbine.

FIG. 3 is a diagram for illustrating a turbine-cooling-medium channelprovided through stationary parts of a turbine.

FIG. 4 is a schematic diagram illustrating a gas turbine according to asecond embodiment of the present invention.

FIG. 5 is a schematic diagram illustrating a gas turbine according to athird embodiment of the present invention.

FIG. 6 is a schematic diagram illustrating a modification according tothe third embodiment illustrated in FIG. 5.

FIG. 7 is a schematic diagram illustrating a gas turbine according to afourth embodiment of the present invention and a ninth embodiment of thepresent invention.

FIG. 8 is a diagram for illustrating a compressor-cooling-medium channelprovided on stationary parts of a compressor.

FIG. 9 is a schematic diagram illustrating a gas turbine according to afifth embodiment of the present invention.

FIG. 10 is a schematic diagram illustrating a gas turbine according to asixth embodiment of the present invention.

FIG. 11 is a schematic diagram illustrating a modification according tothe sixth embodiment illustrated in FIG. 10.

FIG. 12A is a diagram for illustrating an ACC system and illustrates therelationship between time and rotational speed/load.

FIG. 12B is a diagram for illustrating the ACC system and illustratesthe relationship between time and temperature.

FIG. 12C is a diagram for illustrating the ACC system and illustratesthe relationship between time and expansion.

FIG. 12D is a diagram for illustrating the ACC system and illustratesthe relationship between time and clearance.

FIG. 13 is a schematic diagram illustrating a gas turbine according to aseventh embodiment of the present invention.

FIG. 14 is a schematic diagram illustrating a modification according tothe seventh embodiment illustrated in FIG. 13.

FIG. 15 is a schematic diagram illustrating a gas turbine according toan eighth embodiment of the present invention.

FIG. 16 is a schematic diagram illustrating a first modificationaccording to the eighth embodiment illustrated in FIG. 15.

FIG. 17 is a schematic diagram illustrating a second modificationaccording to the eighth embodiment illustrated in FIG. 15.

FIG. 18 is a schematic diagram illustrating a first modificationaccording to the tenth embodiment illustrated in FIG. 1.

FIG. 19 is a schematic diagram illustrating a second modificationaccording to the tenth embodiment illustrated in FIG. 1.

FIG. 20 is a schematic diagram illustrating a gas turbine according toan eleventh embodiment of the present invention.

DESCRIPTION OF EMBODIMENTS

Embodiments of a gas turbine according to the present invention and anoperating method thereof will be described below on the basis of thedrawings.

First Embodiment

FIG. 1 is a schematic diagram illustrating a gas turbine according to afirst embodiment; FIG. 2 is a sectional diagram illustrating, inoutline, the configuration of the gas turbine; and FIG. 3 is a schematicconfiguration diagram illustrating a turbine section of the gas turbine.The illustrated embodiment describes a gas turbine that generates powerby driving a generator. The embodiment, however, is not limited thereto.

The illustrated gas turbine 10 is constituted of a compressor 11, acombustor 12, and a turbine 13, and a generator 14 is connected to theturbine 13. The compressor 11 has an air intake port 15 for taking inair and is constituted of a plurality of stator blades 17 and rotorblades 18 disposed in a compressor cylinder 16 in an alternating mannerand an extraction manifold 19 disposed at the outer side thereof.

The combustor 12 enables combustion by supplying fuel to compressed aircompressed at the compressor 11 and igniting it with a burner.

In the turbine 13, a plurality of stator blades 21 and rotor blades 22are alternately disposed in a turbine cylinder 20.

An exhaust chamber 23 continuous with the turbine cylinder 20 of theturbine 13 is provided, and the exhaust chamber 23 has an exhaustdiffuser 24 continuous with the turbine 13. A rotor (turbine shaft) 25is positioned such that it passes through the centers of the compressor11, the combustor 12, the turbine 13, and the exhaust chamber 23, andthe end thereof on the compressor 11 side is supported by a bearing 26in such a manner that it freely rotates, whereas the end thereof on theexhaust chamber 23 side is supported by a bearing 27 in such a mannerthat it freely rotates. Furthermore, a plurality of disc plates issecured to the rotor 25 to connect the rotor blades 18 and 22, and alsoa driving shaft of the generator 14 is connected to the end of the rotor25 on the exhaust chamber 23 side.

Consequently, the air taken in from the air intake port 15 of thecompressor 11 is compressed into high-temperature, high-pressure air bypassing through the plurality of stator blades 17 and rotor blades 18,and, at the combustor 12, a predetermined amount of fuel supplied tothis compressed air is combusted. Subsequently, the high-temperature,high-pressure combustion gas generated at this combustor 12 rotationallydrives the rotor 25 by passing through the plurality of stator blades 21and rotor blades 22, which constitute the turbine 13, and generatespower by applying a rotational force to the generator 14 connected tothis rotor 25, whereas exhaust gas is released to the atmosphere afterbeing transformed at the exhaust diffuser 24 to have static pressure.

The gas turbine 10, which is configured such that the compressed aircompressed by the compressor 11 coaxial with the turbine 13 is combustedin the combustor 12 by supplying fuel thereto and the generatedcombustion gas is supplied to the turbine 13 to acquire a rotationaldriving force, is provided with, as illustrated in FIG. 1 for example, apressurizing device 40, which extracts, from a cylinder, and pressurizespart of the compressed air passed through the shut down compressor 11 orcompressed at the compressor 11.

As in FIG. 1, the compressed air compressed by the compressor 11 issupplied to the combustor 12 via a compressed-air supply channel 28during startup while the load of the gas turbine 10 is being increasedto achieve rated operation, during rated operation, and during shut-downwhile the load is decreased until shut-down, and the combustion gasgenerated at the combustor 12 is supplied to the turbine 13 via anexhaust channel 29 in a casing. Here, reference numeral 30 in thedrawing represents a fuel supply channel.

The pressurizing device 40 is pressurizing means for pressurizing airused as a heating medium, which is described below, and, for example, isa compressor, blower, etc. Moreover, the pressurizing device 40 includesa dedicated motor 41 and is capable of operating independently from thecompressor 11, which introduces air for carrying out pressurization. Thepressurizing device 40 is desirably shared with, for example, a devicethat compresses and supplies air for cooling the combustor during ratedoperation and so on (pressurizing device for boost-up used for closedcooling).

The intake side of the pressurizing device 40 is connected to abranching channel 42 branching from the compressed-air supply channel 28formed in the cylinder, and the discharge side is connected to atemperature-control-medium supply channel 43. Thetemperature-control-medium supply channel 43 is a channel for guidingcompressed air (pressurized heating medium) to a turbine-cooling-mediumchannel 50 provided in stationary parts of the turbine 13.

For example, as illustrated in FIG. 3, the turbine-cooling-mediumchannel 50 is a channel connecting the turbine cylinder 20, the statorblades 21, and a blade ring 31, and is used for temperature control bycooling and heating by letting a temperature-control medium, such ascompressed air, flow through the blade ring 31, which is specificallydisposed at positions opposing the tips of the rotor blades 22 and whichis a stationary component affecting the tip clearance. The blade ring 31is a member attached to the turbine cylinder 20 in such a manner that itsurrounds the outer circumference of the rotor blades 22.

In other words, in this case, the turbine-cooling-medium channel 50 hasa structure for cooling the blade ring 31 after cooling the statorblades 21 during gas turbine operation, such as rated operation, bycirculating an appropriate temperature-control medium, instead ofcompressed air, which is a pressurizing heating medium; and by lettingcompressed air flow in the turbine-cooling-medium channel 50, it can beused for heating the ACC system. Here, reference numeral 31 a in thedrawing represents a blade-ring channel provided along the entirecircumference of the blade ring 31.

The compressed air that had passed through the turbine-cooling-mediumchannel 50 passes through a temperature-control-medium return channel 44such that the flow is combined with the compressed-air supply channel 28and then flows into the combustor 12 via the compressed-air supplychannel 28.

Therefore, the pressurizing device 40 is operated at startup (duringstartup) of the gas turbine and in preparation immediately beforestartup to let compressed air flow in the turbine-cooling-medium channel50 and is thus capable of raising the temperature of the stationarycomponents in the ACC system.

That is, when the pressurizing device 40 is operated in preparationbefore startup of the gas turbine 10, air, which is a heating medium, istaken in from the air intake port 15 of the compressor 11 and is takenin by the pressurizing device 40 via the inside of the compressor 11,the compressed-air supply channel 28, and the branching channel 42. Thisair is pressurized at the pressurizing device 40 and is transformed intocompressed air, which is a pressurized heating medium with a raisedtemperature, and is then discharged to the temperature-control-mediumsupply channel 43.

The compressed air discharged to the temperature-control-medium supplychannel 43 heats and warms up the stationary components (stationaryparts) of the blade ring 31 etc., while flowing through theturbine-cooling-medium channel 50 in the turbine 13. In particular,since increases in temperature and expansion of the blade ring 31 arecaused by circulating the compressed air through the blade-ring channel31 a of the blade ring 31, which greatly affects the tip clearance, thetip clearance with respect to the rotor blades 22, which are hardlyaffected by heating and whose temperature is not changed, is increased.

In this way, the compressed air that heated the stationary componentsreturns to the compressed-air supply channel 28 via thetemperature-control-medium return channel 44 and, subsequently, isreleased to the atmosphere via a combustion-gas channel of the combustor12 and the turbine 13.

Furthermore, in a similar manner as in the above-described preparationimmediately before startup, the pressurizing device 40 is operated atstartup (during startup) of the gas turbine to raise the temperature byletting the compressed air flow in the turbine-cooling-medium channel50. In such a case, upon starting the operation of the compressor 11,the pressurizing device 40 takes in air, which is a heating medium, fromthe air intake port 15 and introduces part of the main stream ofcompressed air, which has been compressed inside the compressor 11, forpressurization. The main stream of the compressed air in such a state isat a low pressure compared with that during rated operation and so onand is basically supplied to the combustor 12 via the compressed-airsupply channel 28.

However, by operating the pressurizing device 40, part of the mainstream of compressed air is taken in by the pressurizing device 40 viathe branching channel 42. The temperature of the compressed air taken inby the pressurizing device 40 in this way is raised by pressurization bythe pressurizing device 40 and is discharged to thetemperature-control-medium supply channel 43 as compressed air, which isa pressurized heating medium.

In this way, the compressed air discharged to thetemperature-control-medium supply channel 43 is returned to thecompressed-air supply channel 28 via the temperature-control-mediumreturn channel 44 after it flows through the channel in a manner similarto that in preparation immediately before startup, as described above,to heat and warm up the stationary components (stationary parts) of theblade ring 31, etc. That is, since part of the compressed air branchingfrom the main stream of compressed air is used for the purpose ofheating the stationary components and is then returned to thecompressed-air supply channel 28 such that the flows are combined, thefinal amount of air supplied to the combustor 12 is not reduced.

In this way, for tip clearance control by the above-described ACCsystem, since the total amount of air in the main stream of aircompressed at the compressor 11 is collected and supplied to thecombustor 12 without flowing into the gas path side, the decrease incycle efficiency is small, and also the amount of NOx can be reducedsince a large amount of air for combustion can be ensured. Moreover,since the pressurizing device 40, which supplies compressed air used forheating the stationary components, can be independently operated by thededicated motor 41, not only can the gas turbine 10 be independentlystarted up as a single unit, but also the time required for startup canbe reduced. That is, by operating the pressurizing device 40independently from the gas turbine main body at startup of the gasturbine 10, clearance control can be carried out by warming up the bladering 31 by flowing pressurized compressed air to the blade ring 31.

Second Embodiment

Next, a gas turbine according to a second embodiment will be describedon the basis of FIG. 4. Here, parts that are the same as those accordingto the above-described embodiment will be represented by the samereference numerals, and detailed descriptions thereof will be omitted.

The gas turbine 10 according to this embodiment has a bypass channel 45branching from a midpoint in the temperature-control-medium supplychannel 43 and connected to the compressed-air supply channel 28, whichis a discharge-side channel of the compressor 11. Moreover, anopen/close valve 46, serving as channel opening/closing means, isprovided at an appropriate position in the bypass channel 45.

In the gas turbine 10 having such a configuration, by opening theopen/close valve 46 during clearance control of the ACC system, part ofthe compressed air with a higher temperature caused by pressurization bythe pressurizing device 40 can flow into the bypass channel 45. As aresult, the compressed air branching into the bypass channel 45 is takeninto the pressurizing device 40 to be pressurized again.

Accordingly, the temperature of the compressed air supplied to theturbine-cooling-medium channel 50 after pressurization by thepressure-raising device 40 increases even more since pressurizing andheating is carried out again on part of the compressed air, and, thus,the amount of time required for startup of the gas turbine 10 can bereduced correspondingly.

Third Embodiment

Next, a gas turbine according to a third embodiment will be described onthe basis of FIG. 5. Here, parts that are the same as those according tothe above-described embodiment will be represented by the same referencenumerals, and detailed descriptions thereof will be omitted.

In the gas turbine 10 according to this embodiment, a heat exchanger(heating means) 60 that exchanges heat with compressed air, which is aheating medium, to raise the temperature thereof is provided in thebranching channel 42. This heat exchanger 60 carries out heat exchangebetween air flowing through the branching channel 42 before thepressurization and a heating medium flowing through atemperature-control-medium channel 61 and heats the compressed air with,for example, high-temperature steam introduced from an exhaust gasboiler, serving as the heating medium.

Accordingly, the gas turbine 10 including the above-described heatexchanger 60 can increase the temperature of the compressed air passingthrough the turbine-cooling-medium channel 50 even more, and, thus, theamount of time required for starting-up the gas turbine 10 can bereduced correspondingly.

Furthermore, in the modification illustrated in FIG. 6, a heat exchanger62 is provided in the temperature-control-medium supply channel 43, andthe compressed air pressurized at the pressurizing device 40 is heatedby means of a high-temperature heating medium flowing through atemperature-control-medium channel 63. In this way, the temperature ofthe compressed air flowing through the turbine-cooling-medium channel 50can be increased even more, and, thus, the amount of time required forstarting-up the gas turbine 10 can be reduced correspondingly.

Fourth Embodiment

Next, a gas turbine according to a fourth embodiment will be describedon the basis of FIGS. 7 and 8. Here, parts that are the same as thoseaccording to the above-described embodiment will be represented by thesame reference numerals, and detailed descriptions thereof will beomitted.

The gas turbine 10 according to this embodiment has a heating-mediumbranching supply channel 47 that branches from thetemperature-control-medium supply channel 43 and that is connected to acompressor cooling-medium channel 51, and a heating-medium branchingreturn channel 48 that guides the compressed air that has passed throughthe compressor cooling-medium channel 51 to the compressed-air supplychannel 28 such that the flows are combined.

FIG. 8 is a diagram illustrating the outline of the compressorcooling-medium channel 51 provided in the compressor cylinder 16. Thiscompressor cooling-medium channel 51 is a channel for cooling thestationary components of the compressor 11 by letting a cooling mediumflow during normal operation and controls the tip clearance formedbetween the rotor blades 18 of the compressor 11 and the compressorcylinder 16, which is a stationary part.

According to this embodiment, the above-described compressorcooling-medium channel 51 is used at startup of the gas turbine, andthereby clearance control can be carried out on the compressor 11 side.Accordingly, since the temperature of not only the stationary componentsof the gas turbine 10 but also the stationary part on the compressor 11side can be increased, clearance control of the turbine 13 and thecompressor 11 is possible.

Fifth Embodiment

Next, a gas turbine according to a fifth embodiment will be described onthe basis of FIG. 9. Here, parts that are the same as those according tothe above-described embodiment will be represented by the same referencenumerals, and detailed descriptions thereof will be omitted.

The gas turbine 10 according to this embodiment has selective-switchingmeans for heating media on the intake side of the pressurizing device40. In the illustrated example, the pressurizing device 40 includes anatmosphere-intake channel 70 that directly takes in air from theatmosphere and a heating-medium receiving channel 71 that receives thesupply of a high-temperature heating medium, and one of these channelscan be selected by the open/close operation of open/close valves 72 and73, which are selective-switching means in the channels. Here, as ahigh-temperature heating medium, for example, high-temperature air,steam, etc., from an exhaust heat boiler or the like may be introducedand used.

With the gas turbine 10 having such a configuration, in the preparationstep immediately before startup and so on, the temperature can beincreased even more by introducing a high-temperature heating mediumfrom outside the gas turbine 10 if necessary and by pressurizing it atthe pressurizing device 40. Therefore, the stationary components of theturbine 13 can be quickly warmed up using a high-temperaturepressurizing medium, and thus, the amount of time required forstarting-up the gas turbine 10 can be reduced. In this case, thepressurized heating medium that heated the stationary components of theturbine 13 is exhausted as exhaust gas from the turbine 13 and the airintake port 15 of the compressor 11.

Sixth Embodiment

Next, a gas turbine according to a sixth embodiment will be described onthe basis of FIGS. 10 and 11. Here, parts that are the same as thoseaccording to the above-described embodiment will be represented by thesame reference numerals, and detailed descriptions thereof will beomitted.

The gas turbine 10 according to this embodiment has a combustor coolingchannel 80 to which compressed air pressurized at the pressurizingdevice 40 is guided and which is connected in series or in parallel withthe turbine-cooling-medium channel 50. That is, the compressed air forheating the stationary components of the turbine 13 passes through thecombustor cooling channel 80 connected in series or in parallel to coolrequired sections in the combustor 12 and is then guided to thecompressed-air supply channel 28 such that the flows are combined.

In the configuration example illustrated in FIG. 10, the combustorcooling channel 80 is provided in a temperature-control-medium branchingchannel 81 branching from temperature-control-medium supply channel 43,and thus, the combustor cooling channel 80 is connected in parallel withthe turbine-cooling-medium channel 50.

Moreover, in the configuration example illustrated in FIG. 11, as amodification of FIG. 10, the combustor cooling channel 80 is provided inseries with the turbine-cooling-medium channel 50.

With such a configuration, clearance control of the turbine 13 as wellas cooling of the combustor 12 can be carried out using a singlepressurizing device 40. Therefore, in the gas turbine 10 provided with,for example, pressurizing means that extracts part of the compressed aircompressed at the compressor 11 for cooling the combustor 12 and thatsupplies the cooling medium, which is a pressurized form of thiscompressed air, to the combustor 12, the pressurizing means can beshared with the pressurizing device 40 for the above-described ACCsystem. In other words, another pressurizing device 40 does not have tobe provided for the above-described ACC system.

In this way, the gas turbine 10 according to the above-describedembodiments employ the startup operating method described below duringpreparation immediately before startup and at startup.

In other words, carried out at startup of the gas turbine and inpreparation immediately before startup are a step in which thepressurizing device 40, which is connected to the branching channel 42branching from the discharge side of the compressor 11 and which canoperate independently from the compressor, introduces and pressurizesthe air, which is a heating medium; a step in which compressed airpressurized at the pressurizing device 40 is supplied to theturbine-cooling-medium channel 50 provided in the stationary componentsof the turbine 13 to raise the temperature of the stationary componentswith the compressed air passing through the turbine-cooling-mediumchannel 50; and a step in which the compressed air is guided from theturbine-cooling-medium channel 50 to the compressed-air supply channel28 such that the flows are combined.

Accordingly, the compressed air which has an increased temperature dueto pressurization by the pressurizing device 40 heats and warms up thestationary components of the turbine 13 when passing through theturbine-cooling-medium channel 50. At this time, since the pressurizingdevice 40 can operate independently from the gas turbine main body,clearance control can be carried out quickly in preparation immediatelybefore startup, even when the gas turbine main body has not been startedup.

That is, according to the present invention described above, quickoperation control of the ACC system is carried out at startup of the gasturbine and in preparation immediately before startup, and the startupspeed of the gas turbine can be increased. In other words, at startup ofthe gas turbine and in preparation immediately before startup, since ACCcontrol in which the stationary components are expanded by quicklywarming them up to a desired temperature and increasing the clearancebetween the stationary parts and the rotary parts to an optimal value ispossible, the startup speed of the gas turbine can be increased bydecreasing the time required for startup preparation of the gas turbine10. Therefore, the amount of actual operation time during which the gasturbine 10 is operated to drive the generator 14 is increased, and thus,the equipment operation efficiency of the gas turbine 10 is improved.

Furthermore, the effective use of the pressuring means and so on bysharing them for boost-up used for closed cooling realizes high-speedstartup of the gas turbine by performing ACC control with minimumadditional equipment, i.e., without adding new equipment.

Seventh Embodiment

FIG. 13 is a schematic diagram illustrating a gas turbine according to aseventh embodiment. Since the sectional diagram illustrating theschematic configuration diagram of the gas turbine according to thisembodiment and the schematic configuration diagram illustrating theturbine section are the same as those of the first embodiment, thisembodiment will also be described with reference to FIGS. 2 and 3, andparts that are the same as those according to the first embodiment willbe described using the same reference numerals. Here, the illustratedembodiment describes a gas turbine that generates power by driving agenerator. The embodiment, however, is not limited thereto.

The illustrated gas turbine 10 is constituted of a compressor 11, acombustor 12, and a turbine 13, and a generator 14 is connected to theturbine 13. The compressor 11 has an air intake port 15 for taking inair and is constituted of a plurality of stator blades 17 and rotorblades 18 disposed in a compressor cylinder 16 in an alternating mannerand an extraction manifold 19 disposed at the outer side thereof.

The combustor 12 enables combustion by supplying fuel to compressed aircompressed at the compressor 11 and igniting it with a burner.

In the turbine 13, a plurality of stator blades 21 and rotor blades 22are alternately disposed in a turbine cylinder 20.

An exhaust chamber 23 continuous with the turbine cylinder 20 of theturbine 13 is provided, and the exhaust chamber 23 has an exhaustdiffuser 24 continuous with the turbine 13. A rotor (turbine shaft) 25is positioned such that it passes through the centers of the compressor11, the combustor 12, the turbine 13, and the exhaust chamber 23, andits end on the compressor 11 side is supported by a bearing 26 in such amanner that it freely rotates, whereas its end on the exhaust chamber 23side is supported by a bearing 27 in such a manner that it freelyrotates. Furthermore, a plurality of disc plates is secured to the rotor25 to connect the rotor blades 18 and 22, and also a driving shaft ofthe generator 14 is connected to the end of the rotor 25 on the exhaustchamber 23 side.

Consequently, the air taken in from the air intake port 15 of thecompressor 11 is compressed into high-temperature, high-pressure air bypassing through the plurality of stator blades 17 and rotor blades 18,and, at the combustor 12, a predetermined amount of fuel supplied tothis compressed air is combusted. Subsequently, the high-temperature,high-pressure combustion gas generated at this combustor 12 rotationallydrives the rotor 25 by passing through the plurality of stator blades 21and rotor blades 22, which constitute the turbine 13, and generatespower by applying a rotational force to the generator 14 connected tothis rotor 25, whereas exhaust gas is released to the atmosphere afterbeing transformed at the exhaust diffuser 24 to have static pressure.

The gas turbine 10, which is configured such that the compressed aircompressed by the compressor 11 is combusted in the combustor 12 bysupplying fuel thereto and the generated combustion gas is supplied tothe turbine 13 to acquire a rotational driving force, is provided with,as illustrated in FIG. 1 for example, a pressurizing device 40, whichextracts, from a cylinder, and pressurizes part of the compressed airpassed through the shut down compressor 11 or compressed at thecompressor 11.

As in FIG. 13, the compressed air compressed by the compressor 11 issupplied to the combustor 12 via a compressed-air supply channel 28during startup while the load of the gas turbine 10 is being increasedto achieve rated operation, during rated operation, and during shut-downwhile the load is decreased until shut-down, and the combustion gasgenerated at the combustor 12 is supplied to the turbine 13 via anexhaust channel 29 in a casing. Here, reference numeral 30 in thedrawing represents a fuel supply channel.

The pressurizing device 40 is pressurizing means for pressurizing airused as a temperature-control medium (heating medium or cooling medium),which is described below, and, for example, is a compressor, blower,etc. Moreover, the pressurizing device 40 includes a dedicated motor 41and is capable of operating independently from the compressor 11, whichintroduces air for performing pressurization. The pressurizing device 40is desirably shared with, for example, a device that compresses andsupplies air for cooling the combustor during rated operation and so on(pressurizing device for boost-up used for closed cooling).

The intake side of the pressurizing device 40 is connected to abranching channel 42 branching from the compressed-air supply channel 28formed in the cylinder, and the discharge side is connected to atemperature-control-medium supply channel 43. Thetemperature-control-medium supply channel 43 is a channel for guidingcompressed air (pressurized temperature-control medium) to aturbine-cooling-medium channel 50 provided in stationary parts of theturbine 13.

For example, as illustrated in FIG. 3, the turbine-cooling-mediumchannel 50 is a channel connecting the turbine cylinder 20, the statorblades 21, and a blade ring 31, and is used for temperature control bycooling and heating by specifically letting compressed air flow throughthe blade ring 31, which is disposed at positions opposing the tips ofthe rotor blades 22 and which is a stationary component affecting thetip clearance. The blade ring 31 is a member attached to the turbinecylinder 20 in such a manner that it surrounds the outer circumferenceof the rotor blades 22.

In other words, the turbine-cooling-medium channel 50 has a structure inwhich the blade ring 31 is cooled after cooling the stator blades 21during rated operation etc. of the gas turbine 10 by circulatingcompressed air having a relatively low temperature. Furthermore, thisturbine-cooling-medium channel 50 has a structure in which the statorblades 21 and the blade ring 31 are heated and warmed up by lettingcompressed air having a relatively high temperature flow in preparationimmediately before starting up the gas turbine 10, during startup, andduring shutdown. Thus, this turbine-cooling-medium channel 50 can beused for cooling and heating stationary components in the ACC system.Here, reference numeral 31 a in the drawing represents a blade-ringchannel provided along the entire circumference of the blade ring 31.

The compressed air that has passed through the turbine-cooling-mediumchannel 50 passes through a temperature-control-medium return channel 44such that the flow is combined with the compressed-air supply channel 28and then flows into the combustor 12 via the compressed-air supplychannel 28.

Therefore, the pressurizing device 40 is operated during rated operationto let compressed air flow in the turbine-cooling-medium channel 50 andis thus capable of raising the temperature of the stationary componentsin the ACC system.

That is, when the pressurizing device 40 is operated during ratedoperation of the gas turbine 10, air, which is a temperature-controlmedium, is taken in from the air intake port 15 of the compressor 11 andis taken in by the pressurizing device 40 via the inside of thecompressor 11, the compressed-air supply channel 28, and the branchingchannel 42. This air is pressurized at the pressurizing device 40 and istransformed into compressed air (pressurized temperature-control medium)through pressurization by the pressurizing device 40 and is thendischarged to the temperature-control-medium supply channel 43.

The compressed air discharged to the temperature-control-medium supplychannel 43 cools the stationary components (stationary parts) of theblade ring 31 etc., while flowing through the turbine-cooling-mediumchannel 50 in the turbine 13.

The blade ring 31, which temperature is raised by the thermal effect ofthe combustion gas

In particular, since the blade ring 31, which temperature is raised bythe thermal effect of the combustion gas, is cooled by flowing thecompressed air through the blade-ring channel 31 a of the blade ring 31,which greatly affects the tip clearance, the tip clearance with respectto the rotor blades 22 is adjusted so that it is minimized.

In this way, the compressed air that cooled the stationary componentspasses through the temperature-control-medium return channel 44 and isguided to the combustor cooling channel 80, which is connected in serieswith the above-described turbine-cooling-medium channel 50.

The compressed air flowing through the combustor cooling channel 80cools the required section in the combustor 12 and is then guidedthrough the temperature-control-medium return channel 44 to thecompressed-air supply channel 28 such that the flows are combined. Thiscompressed air is used as combustion air of the combustor 12 by beingreturned to the compressed-air supply channel 28. Therefore, the totalamount of compressed air compressed at the compressor 11 is supplied tothe combustor 12. That is, since part of the compressed air branchingfrom the main stream of the compressed air is converged with andreturned to the compressed-air supply channel 28 after being used forthe purpose of cooling stationary components and combustor cooling, theamount of air finally supplied to the combustor 12 is not reduced.

With such a configuration, cooling and clearance control of the turbine13, as well as cooling of the combustor 12, can be carried out using asingle pressurizing device 40. Therefore, in the gas turbine 10 providedwith, for example, pressurizing means that extracts part of thecompressed air compressed at the compressor 11 for cooling the combustor12 and that supplies the cooling medium, which is a pressurized form ofthis compressed air, to the combustor 12, the pressurizing means can beshared with the pressurizing device 40 for the above-described ACCsystem. In other words, another pressurizing device 40 does not have tobe provided for the above-described ACC system. The temperature and thecooling capacity of the compressed air are adjustable by adjusting thepressure and amount of compressed air by operation control of thepressurizing device 40.

Furthermore, in the modification illustrated in FIG. 14, the combustorcooling channel 80 is provided in parallel with theturbine-cooling-medium channel 50. That is, the combustor coolingchannel 80 is provided in the temperature-control-medium branchingchannel 81 branching from the temperature-control-medium supply channel43, and the compressed air, after cooling the combustor 12, convergeswith the flow of the temperature-control-medium return channel 44.

In this way, the gas turbine 10 according to this embodiment includesthe combustor cooling channel 80 connected in series or in parallel withthe turbine-cooling-medium channel 50; and since the compressed air thatcools the stationary components of the turbine 13 passes through thecombustor cooling channel 80 by branching off after cooling or beforecooling, it cools required sections in the combustor 12 and thenconverges with the flow in the compressed-air supply channel 28.

Furthermore, in the embodiment and modification illustrated in FIGS. 13and 14, respectively, the pressure device 40 and its channels are sharedfor cooling of the combustor 12; instead, however, as in the embodimentdescribed below, it may be used exclusively for the ACC system of theturbine 13.

For tip clearance control by the above-described ACC system, since theentire amount of air in the main stream of compressed air compressed atthe compressor 11 is collected and supplied to the combustor 12 withoutflowing into the gas path side, the decrease in cycle efficiency issmall, and, in addition, the amount of NOx can be reduced since a largeamount of air for combustion can be ensured.

Moreover, since the above-described pressurizing device 40 can beindependently operated by the dedicated motor 41, not only is itpossible to start up the gas turbine 10 independently as a single unitin preparation immediately before startup and at startup, but also thetime required for startup can be reduced. That is, by operating thepressurizing device 40 independently from the gas turbine main body atstartup of the gas turbine 10, pressurized and temperature-raisedcompressed air flows through the blade ring 31 to warm up the blade ring31, and thus clearance control can be quickly carried out.

Eighth Embodiment

Next, a gas turbine according to an eighth embodiment will be describedon the basis of FIGS. 15 to 17. Here, parts that are the same as thoseaccording to the above-described embodiment will be represented by thesame reference numerals, and detailed descriptions thereof will beomitted.

The gas turbine 10 according to this embodiment has temperaturecontrolling means for enabling temperature control of a pressurizedtemperature-control medium. The gas turbine 10 illustrated in FIG. 15includes a coolant supply channel 75, as temperature controlling means,that adds a coolant to the temperature-control-medium supply channel 43.The coolant in this case may be either a gas or a liquid; for example,water mist may be added to compressed air for cooling.

As a result, the temperature of the compressed air raised due to thepressurization carried out by the pressurizing device 40 decreases byadding the coolant, and the relative temperature difference with thestationary components to be cooled increases. Accordingly, since thecompressed air can efficiently cool the stationary components due to thelarge temperature difference, cooling efficiency improves even more.

Here, by adding water as a coolant, the cycle efficiency of the gasturbine 10 decreases, but an increase in power output and a decrease inNOx are possible.

Furthermore, in a first modification illustrated in FIG. 16, a heatexchanger 90, which is temperature controlling means, is provided in thetemperature-control-medium supply channel 43. This heat exchanger 90decreases the temperature of compressed air by carrying out heatexchange between a cooling medium flowing through a cooling-mediumchannel 91 and compressed air flowing through thetemperature-control-medium supply channel 43. The cooling medium thatcan be used here includes cylinder air, fuel, supply water to the steamturbine, steam for the steam turbine, and so on.

Furthermore, in a second modification illustrated in FIG. 17, theabove-described heat exchanger 90 is provided in the branching channel42 and decreases the air temperature before pressurization is carriedout by the pressurizing device 40. As the cooling medium in this case,it is also possible to use cylinder air, fuel, supply water to the steamturbine, steam for the steam turbine, and so on.

In this way, by providing the heat exchanger 90, the air temperature ofthe compressed air before pressurization or the compressed airtemperature after pressurization by the pressurizing device 40 can bedecreased through heat exchange with the cooling medium; therefore,efficient cooling is possible due to a lowering in the temperature ofthe compressed air that cools the stationary components during ratedoperation.

Ninth Embodiment

Next, a gas turbine according to a ninth embodiment will be described onthe basis of FIGS. 7 and 8. Since the schematic configuration diagramsof the gas turbine according to this embodiment are the same as thoseaccording to the fourth embodiment, this embodiment will also bedescribed with reference to FIGS. 7 and 8. Here, parts that are the sameas those according to the above-described embodiment will be representedby the same reference numerals, and detailed descriptions thereof willbe omitted.

The gas turbine 10 according to this embodiment has a heating-mediumbranching supply channel 47 that branching from thetemperature-control-medium supply channel 43 and that is connected to acompressor cooling-medium channel 51, and a heating-medium branchingreturn channel 48 that guides the compressed air passing through thecompressor cooling-medium channel 51 to converge with the flow of thecompressed-air supply channel 28.

FIG. 8 is a diagram illustrating the outline of the compressed-aircooling-medium channel 51 provided in the compressor cylinder 16. Thiscompressed-air cooling-medium channel 51 is a channel for cooling thestationary components of the compressor 11 by letting a cooling mediumflow during normal operation and controls the tip clearance between therotor blades 18 of the compressor 11 and the compressor cylinder 16,which is a stationary part.

According to this embodiment, the above-described compressed-aircooling-medium channel 51 is used at startup of the gas turbine, andclearance control can be carried out on the compressor 11 side.Accordingly, since the temperature of not only the stationary componentsof the turbine 10 but also the stationary part on the compressor 11 sidecan be raised, clearance control of the turbine 13 and the compressor 11is possible.

In this way, the gas turbine 10 according to the above-describedembodiment employs the rated-operation operating method during ratedoperation described below.

In other words, the rated-operation method for the gas turbine 10includes a step in which the pressurizing device 40, which is connectedto the branching channel 42 branching from the compressed-air supplychannel 28 of the compressor 11 and can operate independently from thecompressor, introduces and pressurizes air; a step in which compressedair pressurized at the pressurizing device 40 is supplied to theturbine-cooling-medium channel 50 provided in the stationary componentsof the turbine 13 and cools the stationary components with thecompressed air passing through the turbine-cooling-medium channel 50;and a step in which the compressed air is guided to and flows into thecompressed-air supply channel 28 from the turbine-cooling-medium channel50.

Accordingly, during rated operation of the gas turbine, cooling can becarried out efficiently due to the temperature difference between thestationary components of the turbine 13 and the compressed air, andoperation is possible with the tip clearance set to a minimum state. Itis desirable that the compressed air in this case increase coolingefficiency by having a temperature lowered by injecting theabove-described coolant or installing the heat exchanger 90.

In this way, according to the gas turbine and its rated-operation methodaccording to above-described present invention, in the ACC systemoperated during rated operation of the gas turbine, the coolingefficiency of cooling of the turbine stationary components withcompressed air is improved; therefore, the amount of compressed air usedis minimized, and ACC control for maintaining the clearance between thestationary parts and the rotary parts at a minimum can be reliablycarried out. In such a case, effective use of the pressurizing device 40and so on by sharing them for boost-up used for closed cooling enablescontinuous stable rated operation of the gas turbine by carrying outcontrol of the ACC system by minimizing the addition of additionalequipment, i.e., without adding new equipment.

Tenth Embodiment

FIG. 1 is a schematic diagram illustrating a gas turbine according to atenth embodiment. Since the sectional diagram illustrating the schematicconfiguration diagram of the gas turbine according to this embodimentand the schematic configuration diagram illustrating the turbine sectionare the same as those according to the first embodiment, this embodimentwill also be described with reference to FIGS. 2 and 3, and parts thatare the same as those according to the first embodiment will berepresented by the same reference numerals. The illustrated embodimentdescribes a gas turbine that generates power by driving a generator. Theembodiment, however, is not limited thereto.

The illustrated gas turbine 10 is constituted of a compressor 11, acombustor 12, and a turbine 13, and a generator 14 is connected to theturbine 13. The compressor 11 has an air intake port 15 for taking inair and is constituted of a plurality of stator blades 17 and rotorblades 18 disposed in a compressor cylinder 16 in an alternating mannerand an extraction manifold 19 disposed at the outer side thereof.

The combustor 12 enables combustion by supplying fuel to compressed aircompressed at the compressor 11 and igniting it with a burner.

In the turbine 13, a plurality of stator blades 21 and rotor blades 22are alternately disposed in a turbine cylinder 20.

An exhaust chamber 23 continuous with the turbine cylinder 20 of theturbine 13 is provided, and the exhaust chamber 23 has an exhaustdiffuser 24 continuous with the turbine 13. A rotor (turbine shaft) 25is positioned such that it passes through the centers of the compressor11, the combustor 12, the turbine 13, and the exhaust chamber 23, andthe end thereof on the compressor 11 side is supported by a bearing 26in such a manner that it freely rotates, whereas the end thereof on theexhaust chamber 23 side is supported by a bearing 27 in such a mannerthat it freely rotates. Furthermore, a plurality of disc plates issecured to the rotor 25 to connect the rotor blades 18 and 22, and alsoa driving shaft of the generator 14 is connected to the end of the rotor25 on the exhaust chamber 23 side.

Consequently, the air taken in from the air intake port 15 of thecompressor 11 is compressed into high-temperature, high-pressure air bypassing through the plurality of stator blades 17 and rotor blades 18,and, at the combustor 12, a predetermined amount of fuel supplied tothis compressed air is combusted. Subsequently, the high-temperature,high-pressure combustion gas generated at this combustor 12 rotationallydrives the rotor 25 by passing through the plurality of stator blades 21and rotor blades 22, which constitute the turbine 13, and generatespower by applying a rotational force to the generator 14 connected tothis rotor 25, whereas exhaust gas is released to the atmosphere afterbeing transformed at the exhaust diffuser 24 to have static pressure.

The gas turbine 10, which is configured such that the compressed aircompressed by the compressor 11 is combusted in the combustor 12 bysupplying fuel thereto and the generated combustion gas is supplied tothe turbine 13 to acquire a rotational driving force, is provided with,as illustrated in FIG. 1 for example, a pressurizing device 40, whichextracts, from a cylinder, and pressurizes part of the compressed airpassed through the shutdown compressor 11 or compressed at thecompressor 11.

As in FIG. 1, the compressed air compressed by the compressor 11 issupplied to the combustor 12 via a compressed-air supply channel 28during startup while the load is being increased to achieve ratedoperation, during rated operation, and during shut-down while the loadis decreased until shut-down, and the combustion gas generated at thecombustor 12 is supplied to the turbine 13 via an exhaust channel 29 ina casing. Here, reference numeral 30 in the drawing represents a fuelsupply channel.

The pressurizing device 40 is pressurizing means for pressurizing airused as a temperature-control medium (heating medium or cooling medium),which is described below, and, for example, is a compressor, blower,etc. Moreover, the pressurizing device 40 includes a dedicated motor 41and is capable of operating independently from the compressor 11, whichintroduces air for carrying out pressurization. The pressurizing device40 is desirably shared with, for example, a device (pressurizing devicefor boost-up used for closed cooling) that compresses and supplies airfor cooling the combustor during rated operation and so on.

The intake side of the pressurizing device 40 is connected to abranching channel 42 branching from the compressed-air supply channel 28formed in the cylinder, and the discharge side is connected to atemperature-control-medium supply channel 43. Thetemperature-control-medium supply channel 43 is a channel for guidingcompressed air (pressurized temperature-control medium) to aturbine-cooling-medium channel 50 provided in stationary parts of theturbine 13.

For example, as illustrated in FIG. 3, the turbine-cooling-mediumchannel 50 is a channel connecting the turbine cylinder 20, the statorblades 21, and a blade ring 31, and is used for temperature control bycooling and heating by letting compressed air, flow through the bladering 31, which is specifically disposed at positions opposing the tipsof the rotor blades 22 and which is a stationary component affecting thetip clearance. The blade ring 31 is a member attached to the turbinecylinder 20 in such a manner that it surrounds the outer circumferenceof the rotor blades 22.

In other words, the turbine-cooling-medium channel 50 has a structure inwhich the blade ring 31 is cooled after cooling the stator blades 21during rated operation etc. of the gas turbine 10 by letting compressedair having a relatively low temperature flow therethrough. Furthermore,this turbine-cooling-medium channel 50 has a structure in which thestator blades 21 and the blade ring 31 are heated and warmed up byletting compressed air having a relatively high temperature flow inpreparation immediately before starting up the gas turbine 10, duringstartup, and during shutdown. Thus, this turbine-cooling-medium channel50 can be used for cooling and heating stationary components in the ACCsystem. Here, reference numeral 31 a in the drawing represents ablade-ring channel provided along the entire circumference of the bladering 31.

The compressed air that passes through the turbine-cooling-mediumchannel 50 converges with the flow of the compressed-air supply channel28 via a temperature-control-medium return channel 44 and then flowsinto the combustor 12 via the compressed-air supply channel 28.

Therefore, the pressurizing device 40 is operated during shutdown of thegas turbine to carry out ventilation cooling by exhausting thehigh-temperature gas remaining inside the turbine 13. A ventilationcooling system that carries out cooling by ventilating thehigh-temperature gas inside the turbine 13 during shutdown of the gasturbine 10 will be described below.

Since the compressor 11 connected to the turbine 13 is also in ashut-down state during shutdown of the gas turbine 10, when thepressurizing device 40 capable of operating independently from thecompressor 11 is started up, the air taken in from the branching channel42 is pressurized into compressed air, which flows out to thetemperature-control-medium supply channel 43.

This compressed air flows into the compressed-air supply channel 28 viathe temperature-control-medium supply channel 43, theturbine-cooling-medium channel 50, and the temperature-control-mediumreturn channel 44. The compressed air flown into the compressed-airsupply channel 28 flows to the combustor 12 side.

The compressed air flown to the combustor 12 side passes through thecombustor 12 and the turbine 13 and is discharged to the atmosphere. Atthis time, the high-temperature gas remaining in the combustor 12 andthe turbine 13 is discharged to the atmosphere by being pushed out bythe compressed air.

Accordingly, by operating the pressurizing device 40 during shutdown ofthe gas turbine 10, the compressed air pressurized at the pressurizingdevice 40 forcefully discharges the high-temperature gas remaining inthe turbine to the atmosphere, forming a ventilation cooling system thatcarries out quick ventilation cooling. That is, the compressed airflowing through the ventilation cooling system flows through thetemperature-control-medium supply channel 43, the turbine-cooling-mediumchannel 50, and the temperature-control-medium return channel 44 fromthe pressurizing device 40, and then passes through the combustor 12 andthe turbine 13 from the compressed-air supply channel 28 to bedischarged to the atmosphere, thereby ventilating the high-temperaturegas remaining in the combustor 12 and the turbine 13 to carry outcooling thereof.

In the gas turbine 10 according to this embodiment, cat back isprevented during shutdown of the gas turbine 10 by carrying outventilation cooling inside the gas turbine in accordance with anoperating method described below.

That is, the method includes a step in which the pressurizing device 40,which is connected to the branching channel 42 branching from thecompressed-air supply channel 28 of the compressor 11 and which canoperate independently from the compressor 11, introduces air and carriesout pressurization thereof to carry out quick ventilation cooling byforcefully discharging the high-temperature gas remaining in the turbine13 during shutdown of the gas turbine 10; a step in which the compressedair pressurized at the pressurizing device returns to the compressed-airsupply channel 28 via the temperature-control-medium supply channel 43,the turbine-cooling-medium channel 50, and thetemperature-control-medium return channel 44; and a step in which thecompressed air is exhausted to the atmosphere from the compressed-airsupply channel 28 via the combustor 12 and the turbine 13.

Furthermore, modifications such as those illustrated in FIGS. 18 and 19may be employed as the above-described ventilation cooling system.

A ventilation cooling system according a first modification illustratedin FIG. 18 includes an exhaust channel 59 branching from thetemperature-control-medium supply channel 43 and having a firstopen/close valve 65, which is channel opening/closing means, and asecond open/close valve 66, which is provided as channel opening/closingmeans in the temperature-control-medium supply channel 43 at a positiondownstream of the branching point of the exhaust channel 59.

In the ventilation cooling system having such a configuration, the firstopen/close valve 65 is opened and the second open/close valve 66 isclosed while starting up the pressurizing device 40 during shutdown ofthe gas turbine 10. However, during times other than shutdown of the gasturbine 10, the first open/close valve 65 is closed and the secondopen/close valve 66 is opened.

When the pressurizing device 40 is operated during shutdown of the gasturbine 10 in the above-described state, the compressed air pressurizedat the pressurizing device 40 is discharged from the exhaust channel 59to the atmosphere. At this time, since the intake side of thepressurizing device 40 has a negative pressure so that thehigh-temperature gas remaining in the turbine 13 is forcefully suckedand discharged to the atmosphere, ventilation cooling can be quicklycarried out. That is, in the ventilation cooling system in this case,the high-temperature gas flows, from the inside of the high-temperatureturbine 13, back to the branching channel 42 via the exhaust channel 29,the combustor 12 and the compressed-air supply channel 28, to bepressurized at the pressurizing device 40, and is then discharged to theatmosphere from the temperature-control-medium supply channel 43 via theexhaust channel 59 with the first open/close valve 65 opened.

A ventilation cooling system according to a second modificationillustrated in FIG. 19 includes an exhaust channel 64 that branches fromthe branching channel 42 and is provided with a third open/close valve67, which is channel opening/closing means.

In the ventilation cooling system having such a configuration, the thirdopen/close valve 67 is opened while starting up the pressurizing device40 during shutdown of the gas turbine 10. However, during times otherthan shutdown of the gas turbine 10, the third open/close valve 67 isclosed.

When the pressurizing device 40 is operated during shutdown of the gasturbine 10 in the above-described state, the compressed air pressurizedat the pressurizing device 40 passes through the inside of the turbine13, and, in addition, high-temperature gas is taken into the intake sideof the pressurizing device 40. Accordingly, the high-temperature gaspresent in the turbine 13 is forcefully pushed out and sucked in by thecompressed air and is discharged from the exhaust channel 64 to theatmosphere; therefore, ventilation cooling can be quickly carried out.At this time, the intake side of the pressurizing device 40 may have anegative pressure so that the high-temperature gas remaining in theturbine 13 is forcefully pushed out and taken in, or thehigh-temperature gas remaining in the turbine 13 may be forcefullypushed out by providing an intake system 49 in which the pressurizingdevice 40 directly takes in air from the atmosphere.

In this way, when ventilation cooling is quickly carried out bydischarging the high-temperature gas in the turbine 13 to the atmosphereafter the gas turbine 10 is shut down, cat back can be prevented sincethe temperature difference inside the turbine can be alleviated oreliminated.

Furthermore, with regard to additional equipment required for theabove-described cat back prevention, the effective use of the pressuringmeans 40 and so on by sharing them as pressurizing means for boost-upused for closed cooling enables cat back prevention without adding newequipment.

Eleventh Embodiment

Next, a gas turbine according to an eleventh embodiment will bedescribed on the basis of FIG. 20. Here, parts that are the same asthose according to the above-described embodiments will be representedby the same reference numerals, and detailed descriptions thereof willbe omitted.

The gas turbine 10 according to this embodiment operates thepressurizing device 40 during shutdown of the gas turbine 10 and letscompressed air (pressurized temperature-control medium) flow in theturbine-cooling-medium channel 50. That is, unlike the tenth embodimentin which ventilation cooling of the inside of the turbine 13 is activelycarried out, compressed air (including high-temperature gas) flowsthrough the turbine-cooling-medium channel 50 in a circulating mannerby, for example, closing the air intake port 15 of the compressor 11 andthe exhaust side of the turbine 13, when required, to make thetemperature distribution uniform.

That is, high-temperature gas (temperature-control medium) presentinside the combustor 12 and the turbine 13 is taken in forpressurization by operating the pressurizing device 40 and istransformed into compressed air that functions as a pressurizedtemperature-control medium. After this compressed air flows out to thetemperature-control-medium supply channel 43, it is taken into thepressurizing device 40 via the turbine-cooling-medium channel 50, thetemperature-control-medium return channel 44, the compressed-air supplychannel 28, and the branching channel 42. As a result, the compressedair circulates in a closed-circuit channel.

Since compressed air that circulates in this way flows through theblade-ring channel 31 a, which is formed in the blade ring 31, whenpassing through the turbine-cooling-medium channel 50, the temperaturedistribution around the turbine cylinder 20 is made substantiallyuniform along the entire circumference thereof. Thus, since atemperature difference due to convection is less likely to occur insidethe turbine 13 and the entire temperature distribution is madesubstantially uniform, cat back can be prevented.

Furthermore, when compressed air pressurized at the pressurizing device40 is circulated, although the temperature is lowered by heat radiatedfrom the turbine cylinder 20, the internal temperature of the turbine 13can be maintained at a relatively high temperature by circulating thecompressed air having a high temperature due to pressurization. As aresult, for example, with the gas turbine 10 operated in the DSS mode, atemperature drop that occurs during the period from shutdown torestarting operation can be minimized, and, thus, the time required fora warm-up operation, which is required at restart, can be reduced.

In the gas turbine 10 according to this embodiment, cat back isprevented during shutdown of the gas turbine 10 by carrying outventilation cooling inside the gas turbine in accordance with anoperating method described below.

That is, the operating method for when the gas turbine is shut downincludes a step in which the pressurizing device 40, which is connectedto the branching channel 42 branching from the compressed-air supplychannel 28 of the compressor 11 and which can operate independent fromthe compressor 11, introduces air and carries out pressurizationthereof; a step in which the compressed air pressurized at thepressurizing device 40 returns to the compressed-air supply channel 28via the temperature-control-medium supply channel 43, theturbine-cooling-medium channel 50, and the temperature-control-mediumreturn channel 44; and a step in which the compressed air is taken intothe pressurizing device 40 from the compressed-air supply channel 28 viathe branching channel 42.

Therefore, during shutdown of the gas turbine 10, since compressed airflows through the turbine-cooling-medium channel 50 in a circulatingmanner, and this flow extends over the entire circumference of theturbine cylinder 20, the temperature distribution of the inside of thegas turbine 10 is made substantially uniform.

Moreover, it is desirable that the operating method during shutdowndescribed above in the tenth embodiment in which ventilation cooling iscarried out or the operating method during shutdown described in thisembodiment in which the temperature distribution is made uniform bycompressed air circulation be selectively used in consideration of theshutdown period of the gas turbine 10.

Specifically, when the shutdown period of the gas turbine is long, theshutdown operating method in which ventilation cooling is carried outshould be selected, whereas, when the shutdown period of the gas turbineis short, the shutdown operating method using compressed air circulationshould be selected.

By carrying out such selection, the warm-up operation period required atrestart can be shortened because, when the gas turbine shutdown periodis short, such as in the DSS mode, and the gas turbine is restartedafter a short shutdown, lowering of the temperature during the periodfrom shutdown to restarting operation can be minimized. That is, catback prevention, as well as smooth and efficient DSS operation, can becarried out.

In this way, according to the above-described present invention, theoperation required for cat back prevention can be reliably and quicklycarried out by discharging the high-temperature gas in the turbine 13 tothe atmosphere or by maintaining the temperature distribution in theturbine 13 in a substantially uniform state. In particular, when thecompressed air flows in the turbine-cooling-medium channel 50 so as tocirculate therein and the temperature distribution in the turbine 13 ismaintained in a substantially uniform state, even when operation andshutdown of the gas turbine are carried out frequently, such as in theDSS mode, the operation required for cat back prevention can becompleted quickly, and the warm-up operation period at startup can beshortened.

Furthermore, with regard to additional equipment required for cat backprevention, the effective use of the pressuring means 40 and so on bysharing them as pressurizing means for boost-up used for closed coolingenables stable operation shutdown of the gas turbine 10 by performingACC control enabling cat back prevention with minimum additionalequipment, i.e., without adding new equipment.

The present invention is not limited to the embodiments described above;for example, the connection configuration etc., of the compressor andthe turbine may be appropriately modified without departing from thescope of the invention.

REFERENCE SIGNS LIST

-   10 gas turbine-   11 compressor-   12 combustor-   13 turbine-   20 turbine cylinder-   21 stator blade-   22 rotor blade-   28 compressed-air supply channel-   29 exhaust channel-   31 blade ring-   40 pressurizing device-   42 branching channel-   43 temperature-control-medium (heating medium or cooling medium)    supply channel-   44 temperature-control-medium (heating medium or cooling medium)    return channel-   45 bypass channel-   47 heating-medium branching supply channel-   48 heating-medium branching return channel-   50 turbine-cooling-medium channel-   51 compressed-air cooling-medium channel-   60, 62, 90 heat exchanger-   59, 64 exhaust channel-   70 atmosphere-intake channel-   71 heating-medium receiving channel-   80 combustor cooling channel-   75 coolant supply channel

The invention claimed is:
 1. A startup operating method for a gasturbine that supplies combustion gas generated by supplying fuel to acombustor where the fuel is combusted with compressed air compressed ata compressor to a turbine to acquire rotational power and that has anactive clearance control ACC system, the method, which is carried out atstartup of the gas turbine and in preparation immediately beforestartup, comprising: a step in which pressurizing means, which isconnected to a branching channel branching from a discharge-side channelof the compressor and capable of operating independently from thecompressor, introduces and pressurizes a temperature-control medium; astep in which the pressurized temperature-control medium pressurized atthe pressurizing means is supplied to a turbine-cooling-medium channelprovided in a stationary component of the turbine to raise thetemperature of the stationary component with the pressurizedtemperature-control medium passing through the turbine-cooling-mediumchannel; and a step in which the pressurized temperature-control mediumis guided from the turbine-cooling-medium channel to the discharge-sidechannel such that the flows are combined.
 2. The startup operatingmethod for a gas turbine according to claim 1, wherein the pressurizedtemperature-control medium is guided to a blade ring of the turbine.